Intake apparatus of multi-cylinder internal combustion engine

ABSTRACT

An intake apparatus of a multi-cylinder internal combustion engine wherein intake ports communicating with cylinders located at opposite longitudinal ends of a cylinder head are arranged so as to be inclined in a direction toward the longitudinal center of the cylinder head to reduce the longitudinal length of an installing section of the cylinder head for the intake manifold.

FIELD OF THE INVENTION

[0001] This invention relates to an intake apparatus of a multi-cylinder internal combustion engine, and particularly to an intake apparatus of a multi-cylinder internal combustion engine which arranges two intake ports for every one cylinder in the cylinder head and installs an intake manifold.

BACKGROUND OF THE INVENTION

[0002] In a multi-cylinder internal combustion engine, mounted on a vehicle, that arranges more than one cylinder in series, there is known an intake arrangement wherein two intake ports respectively cooperate with each cylinder and are arranged independently in a cylinder head, and cooperate with an intake manifold.

[0003] For example, as shown in FIG. 15, in cylinder head 102 as mounted on a cylinder block (not shown) of a multi-cylinder (for example, four cylinders consisting of first cylinder #1, second cylinder #2, third cylinder #3 and fourth cylinder #4) internal combustion engine, first to fourth fuel injectors 104-1 to 104-4 correspond to each cylinder. And, in manifold installing part 106 to which an intake manifold (not shown) is joined through a gasket (not shown), first low speed side port 108-1A and first high speed side port 108-1B functioning as first intake port 108-1 of first cylinder #1 are formed in the longitudinal direction of cylinder head 102 so that first fuel injector 104-1 is located in the center therebetween, and second low speed side port 108-2A and second high speed side port 108-2B as second intake port 108-2 of second cylinder #2 are formed in the longitudinal direction of cylinder head 102 so that second fuel injector 104-2 is located in the center. Similarly, third low speed side port 108-3A and third high speed side port 108-3B as third intake port 108-3 of third cylinder #3 are formed in the longitudinal direction of cylinder head 102 so that third fuel injector 104-3 is located in the center, and fourth low speed side port 108-4A and fourth high speed side port 108-4B as fourth intake port 108-4 of fourth cylinder #4 are formed in the longitudinal direction of cylinder head 102 so that fourth fuel injector 104-4 is located in the center. In addition, the first low speed side port 108-1A, the first high speed side port 108-1B, the second low speed side port 108-2A, the second high speed side port 108-2B, the third low speed side port 108-3A, the third high speed side port 108-3B, the fourth low speed side port 108-4A and the fourth high speed side port 108-4B are arranged on port centerline “T1” which extends in the longitudinal direction (i.e., the crankshaft axis direction) of cylinder head 102.

[0004] Moreover, in each first to fourth high speed side port 108-1B to 108-4B, first to fourth swirl control valve 110-1 to 110-4 are arranged, respectively. These first to fourth swirl control valve 110-1 to 110-4 are established with a valve constitution body (not shown) between intake port 108 and the intake manifold, that is, between the manifold installation part 106 of cylinder head 102 and an installation flange of the intake manifold, and is fixed to a valve axle 112 to be located on port centerline C1 and which penetrates each first to fourth low speed side port 108-1A to 108-4A, and is opened and closed by turning this valve axle 112. This valve axle 112 is operated by valve actuator 114.

[0005] Moreover, in cylinder head 102, in order to support a delivery pipe (not shown) to distribute fuel to first to fourth fuel injector 104-1 to 104-4, first delivery pipe installing part 116-1, 116-1 corresponding to first cylinder #1, second delivery pipe installing part 116-2, 116-2 corresponding to second cylinder #2, third delivery pipe installing part 116-3, 116-3 corresponding to third cylinder #3, and fourth delivery pipe installing part 116-4, 116-4 corresponding to fourth cylinder #4 are arranged in a predetermined interval parallel to the longitudinal direction of cylinder head 102.

[0006] Examples of such intake apparatus of a multi-cylinder internal combustion engine are disclosed in published Japanese Patent Application Laid-Open Nos. 11-324835, 62-103448, 9-166025, and 8-246884. The intake apparatus of multi-cylinder internal combustion engine disclosed in published Japanese Patent Application Laid-Open No. 11-324835 supports an intake manifold on a cylinder head, and has a rubber gasket between intake manifolds as one set every two cylinders. The intake apparatus of multi-cylinder internal combustion engine disclosed in published Japanese Patent Application Laid-Open No. 62-103448, in the internal combustion engine establishes intake/exhaust valves consisting of three valves every one-cylinder, arranged so that path and hole established corresponding to a cylinder block are located to make a pair and have point symmetry with respect to the center of the cylinder head. The intake apparatus of multi-cylinder internal combustion engine disclosed in published Japanese Patent Application Laid-Open No. 9-166025 in a multi-cylinder internal combustion engine which possesses four valves every one-cylinder, arranges to incline an intake port to either end section of the cylinder head. The intake apparatus of multi-cylinder internal combustion engine disclosed in published Japanese Patent Application Laid-Open No. 8-246884 arranges a valve axle to fix each swirl control valve that arranges to a high-speed side port in an intake port of each cylinder, at the point that takes off from a position of each intake port.

[0007] And, in a traditional intake apparatus of a multi-cylinder internal combustion engine, as shown in FIG. 15, because an entrance end of each intake port (in a surface of manifold installing part that becomes an upstream side opening) is formed in the same shape for each cylinder and on the port centerline “T1”, the intake port of the longitudinal end section side of the cylinder head has been arranged so as to be extended in the longitudinal direction. Accordingly, the manifold installing part of the cylinder head becomes longer in longitudinal direction of the cylinder head, and has been formed in length “L2”, as a result, there is an inconvenience that layout of the engine room of the vehicle becomes more difficult.

[0008] In addition, in FIG. 15, a valve axle for each swirl control valve is arranged to penetrate each low speed side port without a swirl control valve. Accordingly, there are inconveniences in that ventilation resistance in the low speed side port increases and output performance becomes worse.

[0009] To obviate or minimize the above inconvenience, the present invention provides an intake apparatus for a multi-cylinder internal combustion engine, which apparatus arranges two intake ports for each cylinder in a cylinder head of the internal combustion engine which has more than one cylinder in series and mounts an intake manifold to said cylinder, wherein said intake apparatus is arranged to incline each intake port located in the longitudinal end sections of the cylinder head as disposed on opposite sides of a transverse center plane.

[0010] In this invention, an intake apparatus of a multi-cylinder internal combustion engine inclines each intake port as located in longitudinal end sections of the cylinder head, toward the transverse centerline of the cylinder head. Accordingly, a longitudinal length of an installing section of the cylinder head, on which an intake manifold is installed, can be shortened. As a result, the degree of freedom of layout of an internal combustion engine in an engine room is increased.

BRIEF DESCRIPTION OF THE DRAWINGS

[0011] In the drawings:

[0012]FIG. 1 is a plan view of a cylinder head;

[0013]FIG. 2 is an intake side view of the cylinder head taken from the direction of arrow 2 in FIG. 1;

[0014]FIG. 3 is an exhaust side view of the cylinder head taken from the direction of arrow 3 in FIG. 1;

[0015]FIG. 4 is a side view from a chain edge section of the cylinder head shown from the direction of arrow 4 in FIG. 1;

[0016]FIG. 5 is a side view from a supplement apparatus installation side end part of the cylinder head shown from the direction of arrow 5 in FIG. 1;

[0017]FIG. 6 is a bottom plan view of the cylinder head;

[0018]FIG. 7 is a cross-sectional view of the cylinder head taken along line 7-7 in FIG. 6;

[0019]FIG. 8 is a cross-sectional view of a cylinder head taken along line 8-8 in FIG. 6;

[0020]FIG. 9 is an intake side view of the cylinder head taken in the direction of arrow 9 in FIG. 8;

[0021]FIG. 10 is a cross-sectional view of a cylinder head showing successively a cross-section along line 10A-10A in FIG. 4, a cross-section along line 10B-10B in FIG. 8, a cross-section along line 10C-10C in FIG. 8, a cross-section along line 10D-10D in FIG. 7, and a cross-section along line 10E-10E in FIG. 5;

[0022]FIG. 11 is a schematic illustration picking out an intake port and a fuel injector from a cylinder head which is viewed from the top;

[0023]FIG. 12 is a cross-sectional view showing that a piston, a spark plug, a fuel injector and a delivery pipe are installed to the internal combustion engine;

[0024]FIG. 13 is a plan view of a piston;

[0025]FIG. 14 is a partial plan view of a front part of a vehicle; and

[0026]FIG. 15 is a schematic illustration picking out an intake port and a fuel injector from a traditional cylinder head which is viewed from the top.

DETAILED DESCRIPTION

[0027] The present invention will now be described in specific detail with reference to FIGS. 1-14 which illustrate an embodiment of this invention. In FIGS. 12 and 14, reference numeral 2 denotes a vehicle; 4 an engine room; 6 a multi-cylinder (for example, four-cylinder consisting of first #1, second #2, third #3 and fourth #4 cylinders) internal combustion engine; 8 a cylinder block; 10 a cylinder head having two intake ports per cylinder; and 12 a master vacuum device.

[0028] As shown in FIG. 14, in cylinder head 10, at both sides of head centerline or center plane C1 which transversely intersects a longitudinal center part of the cylinder head, a first intake manifold 14-1 corresponding to first cylinder #1 and a second intake manifold 14-2 corresponding to second cylinder #2 are installed to installation flange 16-1 through a gasket (not shown), and a third intake manifold 14-3 corresponding to third cylinder #3 and a fourth intake manifold 14-4 corresponding to fourth cylinder #4 are installed to installed to installation flange 16-2 through a gasket (not shown). Each upstream end of the first to fourth intake manifolds 14-1 to 14-4 is connected to throttle body 18 which is located at about the center part of cylinder head 10.

[0029] The first intake manifold 14-1 diverges downstream into the first low speed side pipe 14-1A and the first high speed side pipe 14-1B. The second intake manifold 14-2 diverges downstream into the second low speed side pipe 14-2A and the second high speed side pipe 14-2B. The third intake manifold 14-3 diverges downstream into the third low speed side pipe 14-3A and the third high speed side pipe 14-3B. The fourth intake manifold 14-4 diverges downstream into the fourth low speed side pipe 14-4A and the fourth high speed side pipe 14-4B.

[0030] In internal combustion engine 6, as shown in FIG. 12, a piston 20 corresponding to each cylinder is arranged, and in cylinder head 10, combustion chamber 22 corresponding to this piston 20 is formed and spark plug 26 is installed in spark plug hole 24 located in this combustion chamber 22. In an upper surface of piston 20, as shown in FIGS. 12 and 13, hollow part 28 is formed to produce a swirl to the intake side. In addition, a fuel jet valve 30 corresponding to each cylinder is respectively installed in cylinder head 10.

[0031] Cylinder head 10, as shown in FIGS. 1-5, includes head joining surface 32 for contact with cylinder block 8, head upper end surface 34 to which a cylinder head cover (not shown) is installed, chain side end part 36 at one longitudinal end, supplement apparatus installation end part 38 at the other longitudinal end, intake side surface 40 along one longitudinal side of head 10, and exhaust side 42 along the other longitudinal side of head 10. In head upper surface 34, intake side cam bearing part 44-1 and exhaust side cam bearing part 44-2 are formed at predetermined intervals.

[0032] Intake side surface 40 of cylinder head 10, as shown in FIGS. 1 and 2, is provided symmetrically on opposite sides of head centerline C1 with intake port flange 46-1 being the manifold installation part that connects first intake manifold 14-1 and second intake manifold 14-2, and second injector installing holes 48-1 and 48-2 corresponding cylinders #1 and #2, being on one side of centerline C1, and intake port flange 46-2 being the manifold installation part that connects third intake manifold 14-3 and fourth intake manifold 14-4, and second injector installing holes 48-3 and 48-4, on the other side of C1. In addition, first delivery pipe installation part 50-1 and 50-1 corresponding to first cylinder #1, second delivery pipe installation part 50-2 and 50-2 corresponding to second cylinder #2, third delivery pipe installation part 50-3 and 50-3 corresponding to third cylinder #3, and fourth delivery pipe installation part 50-4 and 50-4 corresponding to fourth cylinder #4, are arranged in a line in predetermined intervals in the longitudinal direction of cylinder head 10 (see FIGS. 9 and 11). These installation parts 50 are provided to fixedly mount delivery pipe 56 and each fuel injector 30 by fixing bolt 54 that is tightened into screw hole 52 (FIG. 12).

[0033] In cylinder head 10, as shown in FIGS. 1 and 2, intake port flange 46-1 defines therein the upstream ends of first intake port 58-1 corresponding to first cylinder #1 and second intake port 58-2 corresponding to second cylinder #2, and intake port flange 46-2 defines therein the upstream ends of third intake port 58-3 corresponding to third cylinder #3 and fourth intake port 58-4 corresponding to fourth cylinder #4.

[0034] As shown in FIGS. 1 and 6, the first intake port 58-1 consists of first low speed side port 58-1A and first high speed side port 58-1B connecting to combustion chamber 22-1 at the downstream side thereof. The second intake port 58-2 consists of second low speed side port 58-2A and second high speed side port 58-2B connecting to combustion chamber 22-2 at the downstream side thereof. The third intake port 58-3 consists of third low speed side port 58-3A and third high speed side port 58-3B connecting to combustion chamber 22-3 at the downstream side thereof. The fourth intake port 58-4 consists of fourth low speed side port 58-4A and fourth high speed side port 58-4B connecting to combustion chamber 22-4 at the downstream side thereof. The first to fourth low speed side ports 58-1A to 58-4A are formed of a helical shape, and are formed in a shape different from first to fourth high speed side ports 58-1B to 58-4B which are about a true cylindrical shape. The low speed intake ports, where they intersect the mounting surface on the cylinder head, have an elongate or oval configuration, whereas the high speed intake ports have a circular configuration where they intersect the mounting surface.

[0035] As shown in FIG. 2, first low speed side port 58-1A, second low speed side port 58-2A, third low speed side port 58-3A and fourth low speed side port 58-4A are arranged along a low speed side port centerline “C2” which extends in the longitudinal direction of cylinder head 10. Meanwhile, first high speed side port 58-1B, second high speed side port 58-2B, third high speed side port 58-3B and fourth high speed side port 58-4B are arranged along a high-speed side port centerline “C3” that is parallel with but spaced a transverse distance “M” away from the low speed side port centerline “C2”. The low speed side port centerline “C2” is spaced a transverse distance “M1” away from head upper surface 34. The high-speed side port centerline “C3” is distance “M2” away from head surface 34, and the “M2” is bigger than “M1”.

[0036] Further, in intake port flange 46-1, bolt inserting holes 60-1 for fixing the intake manifold are formed. In intake port flange 46-2 bolt inserting holes 60-2 for fixing the intake manifold are formed.

[0037] Meanwhile, in exhaust side 42 of cylinder head 10, as shown in FIG. 3, first to fourth exhaust ports 62-1 to 62-4 that connect to first to fourth combustion chambers 22-1 to 22-4 corresponding to each cylinder are opened. Each exhaust port 62 diverges to one and other side ports at the respective combustion chamber 22 side (see FIG. 6). Moreover, EGR path 64 is provided at supplement apparatus installation end part 38.

[0038] In this embodiment, each intake port 58 associated with each of the longitudinally end-most cylinders (i.e. cylinders #1 and #4) is inclined relative to head centerplane “C1”. In other words, as shown in FIG. 1, first low speed side port 58-1A and first high speed side port 58-1B of first intake port 58-1 located adjacent chain end part 36 are arranged so as to be inclined at an angle “θ1” relative to head centerplane “C1”. Meanwhile, fourth low speed side port 58-4A and fourth high speed side port 58-4B of fourth intake port 58-4 located adjacent supplement apparatus installation end part 38 are arranged so as to be inclined at an angle “θ1” relative to head centerplane “C1”. The angles θ1 for the ports 58-1 and 58-4 are, however, oppositely inclined relative to plane C1, and thus the centerlines for ports 58-1 and 58-4 converge toward one another and individually converge toward the centerplane C1. Accordingly, because the first low speed side port 58-1A and the fourth low speed side port 58-4A are located on opposite sides of head centerline “C1” in the longitudinal direction of cylinder head 10, longitudinal length “L1” (see FIG. 11) between the longitudinal outer edges of the intake port flanges 46-1 and 46-2 can be shorter than conventional length “L2” as shown in FIG. 15.

[0039] Internal combustion engine 6 has more than two cylinders, for example second and third cylinders #2 and #3. These second and third cylinders #2 and #3 that are not located at the longitudinal end sections of cylinder head 10 are divided into two groups “G1” and “G2” (FIG. 1). And, both second low speed side port 58-2A and second high speed side port 58-2B of second cylinder #2 belonging to group “G1” are arranged so as to be inclined at an angle “θ2” relative to centerplane C1. Meanwhile, both third low speed side port 58-3A and third high speed side port 58-3B of third cylinder #3 belonging to group “G2” are also arranged so as to be inclined at angle “θ2” relative to plane C1. The angles θ2 for ports 58-2 and 58-3 are, however, oppositely inclined relative to centerplane C1 and the centerlines for ports 58-2 and 58-3 diverge away from one another and individually diverge away from the centerplane C1. The centerlines for ports 58-2 and 58-3, as defined by the angles θ2, thus are inclined toward the respective end sections 36 and 38 of the cylinder head 10. In addition, the centerlines of the two ports on each side of centerplane C1, such as adjacent ports 58-1 and 58-2, or adjacent ports 58-3 and 58-4, are oppositely inclined. Accordingly, because the second low speed side port 58-2A and the third low speed side port 58-3A are inclined toward opposite ends away from head centerline “C1”, a larger space “S” is formed in between second intake manifold 14-2 and third intake manifold 14-3, and throttle body 18 can be positioned in this space “S”.

[0040] As described above, each intake port 58 consists of low speed side port 58-A and high-speed side port 58-B, and low speed side port 58 is approached to center side of the respective cylinder bore (not shown) and is formed in helical shape. The reason that the low speed side port 58 approaches a center side of the cylinder bore (not shown) and is of helical shape is to improve swirl ratio in low speed driving and to improve combustible property.

[0041] Internal combustion engine 6 is a multi-cylinder internal combustion engine of four cylinders arranged in series. Intake port 58 consists of two groups “H1” and “H2” (FIG. 1) which connect two cylinders for each group in sequence from one longitudinal end of the cylinder head 10, in other words, group H1 which connects first cylinder #1 and second cylinder #2, and group H2 which connects third cylinder #3 and fourth cylinder #4. In each group, the shape of first intake port 58-1 and second intake port 58-2 are symmetrical about first group center axis line or plane “C4” which is transverse to the longitudinal direction of cylinder head 10, and the shape of third intake port 58-3 and fourth intake port 58-4 are symmetrical about second group center axis line or plane “C5” which is transverse to the longitudinal direction of cylinder head 10. Furthermore, the two groups “H1” and “H2” are symmetrical about the group center axis line or plane “C6” as located between groups “H1” and “H2”. This center group center axis line “C6” corresponds to head centerline “C1”.

[0042] As described above, low speed side port 58-A having helical shape and high-speed side port 58-B having about circle shape, as associated with each cylinder, have mutually different shapes. And, distances from head upper surface 34 of cylinder head 10 to about each center of both low speed side and high-speed side ports 58-A and 58-B are “M1” and “M2”, respectively, and are set to be different as described above.

[0043] In between intake port 58 and each intake manifold 14, that is, between each intake port flange 46 and each installation flange 16, as shown in FIGS. 11 and 14, a swirl control valve 68-1 to 68-4 is established by valve constitution body 66. The swirl control valves 68-1 to 68-4 are worked to open and close first to fourth high-speed side ports 58-1B to 58-4B in first to fourth intake ports 58-1 to 58-4. The swirl control valves 68-1 to 68-4 corresponding to each cylinder are fixed to one valve axle 70 so as to open and close simultaneously. The valve axle 70 is located on high-speed side port centerline C3. In addition, because low speed side port centerline C2 is distance “M” away from high-speed side port centerline C3, the valve axle 70 is arranged not to penetrate first to fourth low speed side ports 58-1A to 58-4A, and is operated by valve actuator 72.

[0044] The operation of the above embodiment will now be briefly described.

[0045] Both first and fourth low speed side ports 58-1A and 58-4A, as respectively associated with first and fourth cylinder #1 and #4 as located at longitudinal ends of cylinder head 10, are arranged so as to be inclined at angle “θ1” relative to centerline “C1” direction of cylinder head 10. Accordingly, length “L1” (see FIG. 11) between intake port flanges 46-1 and 46-2 as defined at opposite ends of cylinder head 10 can be shorter than conventional length “L2” (see FIG. 15). As a result, in engine room 4, the degree of freedom of layout of the internal combustion engine 6 is larger.

[0046] Moreover, remaining second cylinder #2 and third cylinder #3 are divided into two groups “G1” and “G2”. And second intake port 58-2 of second cylinder #2 belonging to group “G1” is arranged to be inclined toward first cylinder #1, and third intake port 58-3 of third cylinder #3 belonging to group “G2” is arranged to be inclined toward fourth cylinder #4. Accordingly, as there is no need to connect joining surface with intake manifolds 14 at the upper end opening of intake port 58 of all cylinders in the longitudinal direction of cylinder head 10, the space “S” is formed in between second intake manifold 14-2 and third intake manifold 14-3, and in this space “S” other parts such as throttle body 18 can be positioned. As a result, the intake system is compact as a whole, and while an exhaust reduction apparatus (catalyst, evaporator and the like) becomes large-scale, this invention can contribute to efficient utilization of limited engine room space. Incidentally, when the number of cylinders that are not at the ends of cylinder head 10 is an even number, opened space “S” is located in about the central section of the cylinder head 10 in the longitudinal direction thereof. Accordingly, as shown in FIG. 14, when throttle body 18 is established in this space “S”, the length of an inlet pipe to each cylinder can be equal. As a result, dispersion of intake at each cylinder interval can be reduced, and can improve engine performance.

[0047] Further, because the upstream end of low speed side port 58-A of each cylinder is arranged to be inclined to combustion chamber 22, that is, the direction of the center axis of the cylinder bore, each low speed side port 58-A as it extends between the mounting surface and the combustion chamber can be easily formed in helical shape.

[0048] Furthermore, two groups “H1” and “H2” which connect two adjacent cylinders for each group, in other words, the group “H1” which connects first cylinder #1 and second cylinder #2 and the group “H2” which connects third cylinder #3 and fourth cylinder #4, have linear symmetry between the groups “H1” and “H2”, and, two groups “G1” and “G2” have linear symmetry as well. Therefore, each intake port 58 has the same shape, and a gasket used when connecting intake manifold 14 to end face of intake port 58 can be used in common with two groups “H1” and “H2”. Accordingly, because only one kind of gasket need be used, the number of different parts can be reduced. Moreover, because a gasket is divided every two cylinders, miniaturization of the gasket can be achieved.

[0049] Shapes of both low speed side port 58-A and high-speed side port 58-B that are two intake ports in an end surface, and distances “M1” and “M2” from head upper surface 32 of cylinder head 10, are different, respectively. Accordingly, an integrating mistake when a gasket is mounted can be prevented, and a person who is not mastery of skills can easily mount a gasket, as a result, productivity can be improved.

[0050] Further, in low speed side port 58-A, because valve axle 70 of swirl control valve 68 does not penetrate, ventilation resistance in low speed side port 58-A does not increase, and output performance can be improved.

[0051] Conventionally, in case of a multi-cylinder internal combustion engine, cylinder head 10 has two separated intake ports, and the one intake port 58 of each cylinder is a helical port that is formed in helical shape, and a direction of the helical port of each cylinder is different. In addition, shape of a piston has non-symmetry with respect to center of a cylinder bore as well, and a direction of a piston must be changed for letting direction of helical port fit. Accordingly, pistons of two kinds of shape become necessary. However, in this invention, as shown in FIGS. 12 and 13, because piston 20 can have symmetric shape with respect to a center of the cylinder bore, the piston 20 in all cylinders becomes the same shape. Accordingly, an integrating mistake of the piston 20 is prevented, and kinds of parts can be reduced.

[0052] Incidentally, in this invention, valve actuator 72 is arranged on head centerline C1 (shown with a dashed line of FIG. 11), and valve axle 70 is arranged to be symmetric with respect to this valve actuator 72 in both sides of cylinder head 10, and space of end sections of cylinder head 10 is utilized effectively, and weight balance can be planned because of being symmetric, and can prevent vibration from occurring.

[0053] Although a particular preferred embodiment of the invention has been disclosed in detail for illustrative purposes, it will be recognized that variations or modifications of the disclosed apparatus, including the rearrangement of parts, lie within the scope of the present invention. 

What is claimed is:
 1. An intake apparatus of a multi-cylinder internal combustion engine, which provides two intake ports for each cylinder in a cylinder head having plural cylinders in series and provides an intake manifold for said cylinder, wherein said intake apparatus inclines each intake port as located in longitudinal end sections of said cylinder head relative to a centerline plane which transversely intersects said cylinder head in the longitudinal direction thereof.
 2. An intake apparatus as defined in claim 1 , wherein said internal combustion engine has more than two cylinders, and the cylinders except for the cylinder at the longitudinal ends of the cylinder head are divided into two groups, and both intake ports of the cylinder belonging to one group are arranged to be inclined toward one end of said cylinder head in the longitudinal direction thereof, and both intake ports of the cylinder belonging to the other group are arranged to be inclined toward the other end of said cylinder head in the longitudinal direction thereof.
 3. An intake apparatus as defined in claim 1 , wherein said two intake ports consist of a low speed side port and a high-speed side port, and said low speed side port is formed of helical shape.
 4. An intake apparatus as defined in claim 1 , wherein said internal combustion engine has four cylinders arranged in series, and said intake port consists of two groups which connect two cylinder for each group in sequence from one longitudinal end of said cylinder head, and in each group the shape of each said intake port has symmetry with respect to a group center axis which is perpendicular to the longitudinal direction of the cylinder head, and said two groups have symmetry with respect to a group center axis which is between said two groups and is perpendicular to the longitudinal direction of said cylinder head.
 5. An intake apparatus as defined in claim 1 , wherein said two intake ports are formed of mutually different shapes, and in the intake port opening end surface, distances from an upper surface of said cylinder head to each center of said two intake ports are set to be different, respectively.
 6. An intake apparatus as defined in claim 1 , wherein in between said intake port and said intake manifold, swirl control valves to open and close said high speed side ports in said intake ports are established, each of said swirl control valves is fixed to a common valve axle so as to open and close simultaneously, and the valve axle is arranged so as to not penetrate said low speed side ports.
 7. An intake apparatus of a multi-cylinder internal combustion engine having a cylinder head provided with at least three cylinders disposed in series, first and second said cylinders being disposed at opposite ends of said series and located adjacent opposite longitudinal ends of said cylinder head, said cylinder head having a mounting surface thereon which cooperates with intake manifolds for communication with said cylinders, said intake apparatus including two intake ports formed in said surface and communicating with each respective said cylinder, the two intake ports formed in said surface and communicating with said first cylinder having centerlines which as they project outwardly from the mounting surface are inclined so as to converge toward a center plane which is disposed substantially longitudinally midway between the first and second cylinders and which substantially perpendicularly intersects a longitudinal direction of the cylinder head, and said intake ports associated with said second cylinder being defined by centerlines which as they project outwardly from said mounting surface are inclined so as to converge toward said center plane.
 8. An intake apparatus according to claim 7 , wherein said cylinder head includes third and fourth cylinders which are disposed between said first and second cylinders, said third and fourth cylinders being respectively positioned adjacent said first and second cylinders and positioned longitudinally on opposite sides of said center plane, each of said third and fourth cylinders having two intake ports respectively associated therewith and formed in said mounting surface, the intake ports associated with each of said third and fourth cylinders being defined by centerlines which as they project outwardly from said mounting surface are inclined so as to diverge away from said center plane.
 9. An intake apparatus according to claim 8 , wherein said mounting surface includes first and second flat surface areas defined on opposite sides of said center plane, said first flat surface area having the intake ports associated therewith as corresponding to said first and third cylinders, and said second flat surface area having the intake ports associated therewith which correspond to said second and fourth cylinders.
 10. An intake arrangement according to claim 9 , wherein a first said intake port as associated with each said cylinder has a generally circular configuration at said mounting surface, and wherein a second said intake port as associated with each said cylinder has an oval configuration at said mounting surface.
 11. An intake arrangement according to claim 9 , wherein the first intake ports associated with said plurality of cylinders are disposed with centers thereof located on a first centerline which extends generally parallel with the longitudinal direction, and the plurality of second intake ports associated with said cylinders are disposed with centers thereof located on a second centerline which is generally parallel with and spaced transversely from said first centerline.
 12. An intake apparatus according to claim 11 , wherein the first intake ports associated with the adjacent first and third cylinders, and the first intake ports as associated with the adjacent second and fourth cylinders, are positioned closely adjacent one another in the longitudinal direction and are positioned longitudinally between the second intake ports associated with the pair of adjacent first and third cylinders and as associated with the pair of adjacent second and fourth cylinders. 